Transmission



Sept. 19, 1961 E. c. BULLARD ETAL 3,000,228

TRANSMISSION 5 Sheets-Sheet 1 Original Filed Jan. 31, 1955 FIG.|

FIG.2

ATTORNEY EDWARD C. BULLARD ARTHUR A. TOMENOEAK Sept. 19, 1961 E. c.BULLARD ETAL 3,000,228

TRANSMISSION 5 Sheets-Sheet 2 Original Filed Jan. 31, 1955 INVENTORS.

F G 1 3 EDWARD C. BULLARD ARTHUR A. TOMENCEAK ATTORNEY Sept. 19, 1961 E.c. BULLARD ET AL 3,000,228

TRANSMISSION Original Filed Jan. 31, 1955 5 Sheets-Sheet 3 FIG.5

INVENTORS. EDWARD C. BULLARD ARTHUR A. TOMENCEAK ATTORNE Sept. 19, 1961E. c. BULLARD EI'AL 3,000,228

TRANSMISSION Original Filed Jan. 31, 1955 5 Sheets-Sheet 4 FIG. 6

INVENTORS. EDWARD C. BULLARD ARTHUR A TOMENGEAK ATTORNEY Sept. 19, 1961E. c. BULLARD ETAL 3,000,228

TRANSMISSION Original Filed Jan. 31, 1955 5 Sheets-Sheet 5 FIG.?

FIG.8

INVENTORS. EDWARD C. BULLARD ARTHUR A. TOMENGEAK ATToRN EY United StatesPatent 3,000,228 TRANSMISSION Edward C. Bullard, Southport, and ArthurA. Tomenceak and James E. Ettorre, Fail-field, Conn., assignors to TheBullard Company, a corporation of Connecticut Original application Jan.31, 1955, Ser. No. 484,998, now Patent No. 2,947,188, dated Aug. 2,1960. Divided and this application Nov. 10, 1959, Ser. No. 852,002

7 Claims. (Cl. 74-364) and fine rates of output rotation may beaccomplished a;

in order to produce coarse and fine rates of feed for a tool of amachine tool.

Another object of the invention is to providesuch transmission includinga controller adapted to render mined intervals and in a predeterminedorder.

Another object of this invention is to provide such a transmission inwhich a relatively rapid output speed is also produced as well as thecoarse and fine rates in order to move a tool at a relatively rapidtraverse rate.

Another object of the invention is to provide such a transmission inwhich the relatively rapid output is rendered effective by frictionclutch means, and the coarse and fine speeds are rendered effective bypositive clutch means.

Another object of the invention is to provide such a transmission inwhich the clutches are hydraulically operated.

The above, other objects and novel features of the invention will becomeapparent from the following specification and accompanying drawingswhich are. merely exemplary.

In the drawings:

RIG. 1 is a top plan view of a feedworks transmiseifective said coarseand fine feed output, at predetersion to which the principles of theinvention have been applied; FIG. 2 is a sectional elevational viewtaken substantially along line 22 of FIG. 1; 1

FIG. 3 is a stretch-out sectional elevational view of the transmission.shown in FIGS. 1 and 2;

FIG. 4 is a sectional elevational view taken substantially along line 44of FIG. 3;

FIG. 5 is a sectional plan view taken substantially along line 55, ofFIG. 2;

FIG. 6 is a sectional elevational view taken substantially along line6-6 of FIG. 3, but rotated counterclockwise through 90";

FIG. 7 is an elevational view of a controller for the transmission shownin FIG. 1; and v FIG. 8 is a sectional view taken substantially alongline 8-8 of FIG. 7.

Referring to FIG. 3, which is a stretch-out showing of a feedworkstransmissionF, power is adapted to supplied to it from a bull gear 99(see also FIG. 1) which receives its power from an electric motoror jthe like through a speed reductionunit not shown. One gear 100 of acluster gear is in mesh with the bull gear 99, and the other gear 101thereof meshes with a gear 102 on a back shaft 103 of the transmissionF. I Another gear 104 splined to the back shaft 103 meshes with a gear105 that is fixed to a vertically-disposed shaft 106. The shaft ,106'has fixed to it a worm 107 that meshes with a worm gear 108 (FIGS. 1 and2) that is fixed to a shaft 109; A spur gear 110' is fixed to the shaft109 and itvmeshes with a gear 110 integral with a sleeve 111 that isfreely rotatable about the axis of a shaft 112. The sleeve element 111is provided with positive clutch engaging teeth 113 and 114 on oppositeends thereof. A shift'able'clutch spool 115 having positiveclutchengaging teeth 116 is splined to the shaft 112 and is adapted to bemoved rightwardly (FIG. 5) to connect the gear 110 to the shaft 112, andto be moved leftwardly to, disengage the gear 110 from shaft 112.Another clutch shifting element 117 having positive clutch engagingteeth 118 is splined to a sleeve 119 that is freely rotatable about theaxis of the shaft 112. The clutch element 117 is adapted to be movedleftwardly (FIG. 5) to connect the gear 110 to the splined sleeve 119,and to be moved rightwardly to disengage the gear 110 therefrom.Referring, to FIG. 5, a housing 120 .for the feedworks F supports a drawbar 121. The draw bar 121 has clutch shifting fingers 122 and 123 fixedto it, which cooperate with the clutch shifting elements 115 and 117,respectively. The draw bar 121 has fixed to its one end a piston, '124that'is adapted to be reciprocated within a cylinder attached to thebracket 120. Liquid under pressure is adapted to be admitted to thecylinder 125 on the lefthand side of the piston 124 by a line 127.Accordingly, admission of liquid under pressure to the cylinder 125 fromthe line 126 will cause the gear 110 to be connected to the shaft 112;and, admission of liquid under pressure to the cylinder 125 through theline 127 will cause the gear 110 to be connected to the splined sleeve119.

.Referring again to FIG. 2, a spur gear 128 is keyed to the sleeve 119and a different ratio gear 129 is keyed to the shaft 112. Gears 128 and129 mesh with gears 130 and 131, respectively, both of which latter arekeyed to a shaft 132 parallel to shaft 112. It is evident that the ratioof feed between the shaft 109 and the shaft 132 can be preset for coarseand fine feed by placing the proper gears on the shaft '112, the sleeve119 and the shaft 132 Theshaft 132is provided with the usual "type ofrattle clutch 133 for safety purposes, and the end of the shaft 132opposite that to which the gears 130 and 131 are connected has fixed toit a bevel pinion 134. Bevel pinion 134 meshes with a bevel gear 135fixed to a stub shaft 136 that extends upwardly above the top of thefeedworks F. A spur pinion 137 is fixed to the stub shaft 136 on the topof the feedworks F and it meshes with a spur gear 138 (FIGS. 1 and 3)that is keyed to a vertically-disposed shaft 139 parallel with the shaft106, and extending downwardly into the hous ing of the feedworks F.

Referring to FIGS. 3 and 4, the shaft 139 is arranged in parallelrelation with respect to a screw 83. The shaft 139 is provided with aclutch shifting element 140 that is splined thereto and includespositive-action clutch teeth 141. The shaft 139 also supports a spurgear 142 for free rotation thereon. The gear 142 meshes with a similarspur gear 143 (FIG. 3) that is keyed to a shaft 144 coaxial with thescrew 83 and parallel with the shaft 139. Shaft 144 is coupled to thescrew 83 by a sleeve coupling 145. Referring to FIG. 4, the clutch .140is connected to a clutch-shifting finger 146 that is fixed to a pistonrod 148, which latter extends into a cylinder 149 arranged in parallelrelation relatively to the shaft 139. The piston rod 148 is integralwith a piston 150. Within the cylinder 149 and in line with the piston.150, an auxiliary piston 151 is located. The

piston 151 provided with an enlarged portion 152 and a smaller diameterportion 153 for .a purpose to be described later. The cylinder 149 hasits end opposite that receiving the piston rod 148 closed by a fixedplug 154 having a portion of reduced diameter 155.. Ports 156, 157 and158 admit liquid under pressure to the cylinder 149. Constant pressureliquid is adapted at all times to be admitted to the cylinder 149through the port 158 from a line 159, thereby acting on the effectivearea of the piston 150. When the ports 156 and 157 are :open to'exhaust,pistons 150 and 15 1 are urged .leftwardly .(FIG. 4') into abuttingrelation with the smaller diameter portion 155 of the plug 154, therebymaintaining the positive action clutch teeth 14 1 out of engagement withthe positive action clutch teeth of "the gear 142. v

'Ihe ports 156 and 1 57 in the cylinder 149 are connected to lines 160and 16 1, respectively. The admission of liquid to either of the lines160 and 161 will cause the [piston 148 to move rightwardly (FIG. 4') andthe clutch 140 downwardly (FIG. 3 thereby effecting engagement betweenclutch teeth 141 and those on the gear 142 to thereby cause the rotationof the screw '83 and to move a tool head downwardly.

Referring again to 2,, it will benoted that the two sets of transfergears 128, 130 and129', 131=providefast and slow rates of rotation ofthe shaft'1-32, respectively. Should the clutch 117 be connected to gear110, gears 128 and 130 rotate the shaft 132 at a relatively rapid rate;and should the clutch 115 be engaged with the gear 1 10, the shaft 132is rotated through the gear train 129 and 131 at a -relatively slowrate. From the foregoing, it is evident that the tool headcan be fed ata .fast or slow rate depending upon whether clutch 117 or 115 isconnected to gear 110. Of course, the gears 128, 129, 130 and 141 arechange'or transfer gears and any desired feed rates can be provided byselecting the proper gear ratio between shaft-s 112 and Referring againto FIG.- 3, the gear '102 meshes with a gear 162 journaled on the shaft144. This gear 102 also meshes with a gear 163 that is fixed to a shaft164 parallel with the shaft 144. 'Another gear 165 fixed to shaft "164meshes with a gear 166 journaled on the shaft 144. Y

From the foregoing, it is evident that the gears 162 and 166 rotate inopposite directions at relatively fast rates of speed, as distinguishedfrom the speed at which the gear 143 can be rotated. A shiftable clutchmechanism 167 is splined to the shaft 144 and is provided with friction,clutch-engaging portions 168 and 169 that are adapted to cooperate withmating clutch-engaging surfaces170 and 171 fixed to the gears 162 and166,

respectively. The shifting of the clutch element 167 upwardly anddownwardly will effect the relatively rapid rotation of the screw 83 tothereby provide a rapid traverse rate of motion of the tool head eitherupwardly or downwardly.

Referring to FIG. 6, a clutch shifting finger 172 is provided with aroller 173 that cooperates with a groove Within the clutch mechanism167. The finger 172 is fixed to a shaft 174 to the one end of which isattached a piston 175 that is adapted to be reciprocated within acylinder 176; Finger 172 is likewise fixed to a piston rod 177 parallelwith the shaft .174 and extending into a cylinder 178. Pistons 179 and180 are slidably mounted on the rod 177 within the cylinder 178. The rod177'is provided with a shoulder 181 that cooperates with the piston 179,and a washer 182 that cooperates with "the piston 180. Cylinder 178'is"provided with a port 183 connected to a line 1 84 through which liquidunder constant pressure is continuously adapted to be supplied. Theconstruction andarrangement of' the,

:parts are such that the pistons 179*and 180- are constantly urgedapart, normally -maintaining-the 'OhlfQh 167 in a neutral position. Thecylinder 176 is provided with ports 185 and 186 connected to lines 187and 188, respectively. The ports 185 and 186 are located on oppositesides of the piston so that the admission of liquid under pressure tothe cylinder 176 through the line 187 will cause piston 175 to moverightwardly (FIG. 6) since the effective area of the piston 175 issubstantially greater than the effective area of the pistons 1.79.Rightward movement of piston 175 will effect the engagement of theclutch elements 169 and 171 to cause the screw 83 to rotate in arelatively rapid rate in one direction. Admission of liquid underpressure to the line 188 and exhausting the liquid in line 187 causesthe piston 175 to move leftwardly (FIG. 6) thereby effecting theengagement of the clutch elements 168 and 170, whereupon the screw '83is caused to rotate in a reverse direction at a relatively rapid rate.Exhausting" both the lines 187 and 188 immediately causes the-pressurewithin the line 184 to neutralize the clutch I67.

Referring to FIGS. 7 and 8, the feedworks F is provided with a separatecontrol C Referring to FIG. 3, a-worin 242 integral with gear 142 mesheswith a worm gear 243 fixed to a shaft 244. Referring to FIG. '8, theshaft 244 is connected to a shaft 245 by a universal joint 246. Theshaft 245 extends into a housing 247 of the control C and has keyed toit acontrol drum 248. The

248 is made up of a'plurality of individual discs 250 and 251- .formingbetween adjacent ones, grooves 252,253, 254-and'255. Dogs 256 areadapted adjustably to be located peripherally around the drum 248 in theslots 252' to 255. Also located within the housing 247 is asupport 257on which is mounted a switch box 257 containing switches 2'58, 259, 260,261, 262, 263 and .264. The peripheral dimension of the drum isproportional to the travel of the tool head, and since there is 'apositive geared drive between the screw 83 and the 248, it is evidentthat every point about the drum corresponds to a point in the travel ofthe head. Accordingly, presetting a dog 256 in the slot 252 tosimultaneously operate switches 258 and 259 will stop upward traversemovement of the tool head. The switches 260 and 261 within the switchbox 257 are adapted to control the extent of coarse feed, and theswitches 262, 263 are adapted to control the duration of fine feed.These two feeds, as previously described, are effective by the shiftingof the clutches 115 and 117 (FIG. 5). The switch 264 within the switchbox 257 is a timer switch.

Although the various features of the new and improved transmission havebeen shownand described in detail to fully disclose one embodiment ofthe invention, it will be evident that numerous changes may be made insuch details and certain features may be used without others withoutdeparting from the principles of the invention.

What is claimed is:

1. In a transmission; first and second parallel shafts; intermeshingtransfer gears keyed to said shafts for changing-the relative rotationof one to the other; a third shaft; a reversible gear drive connectingsaid first shaft and said third shaft; parallel power paths connectingsaid second shaft and said third shaft; and transfer gears in each ofsaid parallel power paths for changing the relative rotations of saidthird and second shafts.

2. In a transmission, first and second parallel shafts; intermeshingtransfer gears keyed to said shafts for changing the relative rotationof one to the other; a third shaft; a reversible gear drive connectingsaid first shaft and said third shaft; parallel power paths connectingsaid second shaft and said third shaft; transfer gears in each "of saidparallel power paths for changing the relative "rotations of said thirdand second shafts; and selectively operable clutches'within' said powerpaths for connecting the transfer'gears in' each path to said secondshaft.

3. In a transmission, first and second parallel shafts; intermeshingtransfer gears keyed to said shafts for changing the relative rotationof one to the other; a third shaft; a reversible gear drive connectingsaid first shaft and said third shaft; parallel power paths connectingsaid second shaft and said third shaft; transfer gears in each of saidparallel power paths for changing the relative rotations of said thirdand second shafts; selectively operable clutches said power paths forconnecting the transfer gears in each path to said second shaft; and aclutch for connecting and disconnecting a selected one of said transfergears in said parallel power paths to said third shaft.

4. In a transmission, first and second parallel shafts; intermeshingtransfer gears keyed to said shafts for changing the relative rotationof one to the other; a third shaft; a reversible gear drive connectingsaid first shaft and said third shaft; parallel power paths connectingsaid second shaft and said third shaft; transfer gears in each of saidparallel power paths for changing the relative rotations of said thirdand second shafts; selectively operable fluid-operated clutches withinsaid power paths for connecting the transfer gears in each path to saidsecond shaft; and a fluid-operated clutch for connecting anddisconnecting a selected one of said transfer gears in said parallelpower paths to said third shaft.

5. In a transmission, first and second parallel shafts; inter-meshingtransfer gears keyed to said shafts for changing the relative rotationof one to the other; a third shaft; a reversible gear drive connectingsaid first shaft and said third shaft; parallel power paths connectingsaid second shaft and said third shaft; transfer gears in each of saidparallel power paths for changing the rela tive rotations of said thirdand second shafts; a control drum geared to said third shaft; and dogson said control drum for rendering effective said parallel power pathsin a predetermined order.

6. In a transmission, first and second parallel shafts; intermeshingtransfer gears keyed to said shafts for changing the relative rotationof one to the other; a third shaft; a reversible gear drive connectingsaid first shaft and said third shaft; parallel power paths connectingsaid second shaft and said third shaft; transfer gears in each of saidparallel power paths for changing the relative rotations of said thirdand second shafts; selectively operable clutches within said power pathsfor connecting the transfer gears in each path to said second shaft; aclutch for connecting and disconnecting a selected one of said transfergears in said parallel power paths to said third shaft; a control drumgeared to said third shaft in a manner to be unaffected by saidlast-mentioned clutch; and dogs on said control drum for renderingeflective all of said clutches in a predetermined order.

7. In a transmission, first and second parallel shafts; intermeshingtransfer gears keyed to said shafts for changing the relative rotationof one to the other; a third shaft; a reversible gear drive connectingsaid first shaft and said third shaft; parallel power paths connectingsaid second shaft and said third shaft; transfer gears in each of saidparallel power paths for changing the relative rotations of said thirdand second shafts; selectively operable fluidoperated clutches withinsaid power paths for connecting the transfer gears in each path to saidsecond shaft; a fluid-operated clutch for connecting and disconnecting aselected one of said transfer gears in said parallel power paths to saidthird shaft; a control drum geared to said third shaft in a manner to beunaffected by said last-mentioned clutch; and dogs on said control drum.for rendering effective all of said clutches in a predetermined order.

References Cited in the file of this patent UNITED STATES PATENTS2,557,896 Soule et al June 19, 1951 2,701,477 Schoepe Feb. 8, 19552,712,140 Curtis et al July 5, 1955 2,774,250 Gallimore Dec. 18, 1956

